CN106132600B - Lathe - Google Patents

Abstract

This invention provides a machine tool capable of accurately and precisely machining even relatively large workpieces. The machine tool (1) of this invention includes a first rotating member (10), a surrounding portion (48), a first track (58), a second track (56), and a fitting member (66). The surrounding portion (48) surrounds the first rotating member (10). The first track (58) is disposed on the first rotating member (10). The second track (56) is disposed on the surrounding portion (48) such that it is aligned with the first track (58) at a predetermined rotational position. The fitting member (66) moves along the first track (58) and the second track (56), and in a first state engages with both the first track (58) and the second track (56), and in a second state engages with the second track (56) but not with the first track (58).

Description

machine tool

technical field

The invention relates to a machine tool.

Background technique

In a machining device (machine tool) such as a CNC lathe, in order to rotate a spindle holding a workpiece, a motor integral with the spindle is generally incorporated in a spindle housing. Since the motor directly drives the spindle, no gear transmission is required. The drive mechanism driven by this motor performs turning processing such as removing the outer diameter portion of the workpiece by rotating the spindle at high speed. In addition, in order to perform C-axis contouring etc. with the same motor, it is necessary to precisely control the rotation angle and rotate the spindle at a low speed. However, this motor is not suitable for manufacturing from the viewpoint of practicality and economy when machining a workpiece such as a spindle through hole having a certain size or more. In lathes aimed at machining such workpieces, another motor with a gear transmission mechanism is used to rotate the spindle. However, even with such a driving structure, the positioning accuracy of the rotation angle of the main shaft is lowered due to backlash or backlash in the gear transmission mechanism. Therefore, it is not suitable to use a drive mechanism with a gear transmission mechanism for high-precision mechanical operations such as C-axis contouring.

It is known in the technical field to use two independent motors in the drive of a rotary table supporting a workpiece to be machined, as in a vertical machining center. For example, the turntable is driven by one motor for high-speed and medium-speed rotational motions and a servo motor for low-speed rotational or angular indexing motions. In this system, the motors on both sides are connected to the rotating parts by means of a gear transmission mechanism. This drive configuration is also less suitable for contouring applications due to inaccuracies introduced by the gear transmission mechanism. In addition, there are Patent Document 1 and Patent Document 2 as prior art related to the present invention, for example.

Patent Document 1: Japanese Patent Laid-Open Publication No. Sho 63-191549

Patent Document 2: Japanese Patent Laid-Open Publication No. 2003-170334

Machine tools are expected to perform accurate and high-precision machining of workpieces.

Contents of the invention

An object of the present invention is to provide a machine tool capable of processing workpieces accurately and with high precision.

In order to achieve the above object, the machine tool of the present invention performs processing using rotation, which includes: a first rotating part, which rotates around the rotating shaft; a surrounding part, which surrounds the first rotating part; a first track, which is arranged on the A first rotating member; a second rail disposed on the surrounding portion so as to be aligned with the first rail at a predetermined rotational position; and a fitting member along the first rail and the first rail. The second track slides, and is fitted with the first track and the second track in the first state, and is not fitted with the first track but fitted with the second track in the second state. combine.

The machine tool of the present invention performs machining using rotation, which includes: a first rotating part, which rotates around a rotating shaft; a surrounding part, surrounding the first rotating part; a first track, arranged on the first rotating part; A second rail is provided on the surrounding portion so as to be arranged on the same line as the first rail at a predetermined rotational position; and a fitting member moves along the first rail and the second rail, And in the first state, it fits with the first rail and the second rail, and in the second state, it does not fit with the first rail but fits with the second rail.

Therefore, the fitting member can move along the first track and the second track, and transfer from the second state to the first state. That is, it is possible to achieve a structure in which the fitting member is fitted to the first rail and the second rail, and the first rotating member is fixed relative to the surrounding portion. Therefore, since the fitting member is fitted to the first rail and the second rail, it is possible to prevent a gap from being generated between the fitting member and each rail (in other words, it is possible to prevent play or the like from being generated). Therefore, since the rotation of the first rotating member can be controlled with high precision, the workpiece can be machined accurately and with high precision.

Description of drawings

FIG. 1 is a perspective view of a machine tool omitting an illustration of a tool post unit.

Fig. 2 is a perspective view showing a spindle portion of the machine tool.

FIG. 3 is a schematic diagram showing the configuration of a spindle drive system.

Fig. 4 is a perspective view showing the configuration of a spindle drive system.

Fig. 5 is a diagram showing a configuration of main parts of a second transmission mechanism.

Fig. 6 is an enlarged perspective view showing a structure including a lock mechanism in an unlocked structure.

Fig. 7 is an enlarged side view showing the configuration of the fitting member and each rail in the locked configuration.

Fig. 8 is an enlarged perspective view showing the configuration of the fitting member and each rail in the locked configuration.

Fig. 9 is a perspective view showing the structure of a second transmission mechanism connected to the main shaft.

Fig. 10 is a perspective view showing the main shaft rotated in the clockwise direction by the second motor.

Fig. 11 is an enlarged side view showing the configuration of the fitting member and each rail in the unlocked configuration.

Fig. 12 is an enlarged perspective view showing the configuration of the fitting member and each rail in the unlocked configuration.

Fig. 13 is a perspective view showing a connection structure in which the second transmission mechanism is separated from the main shaft.

Fig. 14 is a perspective view showing the main shaft rotated in the clockwise direction by the first motor.

Fig. 15 is a side view showing the configuration of the spindle drive system.

Explanation of reference signs

1 machine tool

4 spindle drive system

8 workpieces

10 spindles

12 First motor

14 Second motor

16 Spindle housing

18 First delivery agency

20 gearbox

38 Second delivery agency

44 hob cam unit

46 cam roller

48 turret unit

52 locking mechanism

54 Third track

56 Second track

58 First track

62 outer wheel member

64 Inner wheel member

66 Fitted components

68 hydraulic actuator

70 contact part

72 Convex

74 Cam follower

AX rotation axis

detailed description

In one form, a machine tool with a spindle drive has a spindle, a first electric motor and a first transmission. The spindle is used to hold and rotate the workpiece around its axis. The first motor can drive the spindle. The first transmission mechanism is operatively connected between the main shaft and the first motor, so that the first motor can drive the main shaft. The machine tool also has a second motor and a second transmission mechanism. The second motor is capable of driving the spindle. The second transmission mechanism is operatively connected between the main shaft and the second motor, so that the second motor can drive the main shaft. The second transfer mechanism includes a selectively fixable transfer element. The transfer element is mounted around the main shaft with a free structure. The transmission element can freely rotate around the main shaft by not connecting the second motor to the main shaft. In addition, the second transmission mechanism includes a fixing structure, and the transmission element is fixed relative to the main shaft in such a manner that the second motor is operatively engaged with the main shaft. When the machine tool uses the second motor to drive the spindle, it can perform high-precision milling of workpieces. When used with a larger spindle size, this machine tool is capable of higher precision C-axis milling than machines with known large spindle drive systems.

In one aspect, the second transmission mechanism has a plurality of cam followers such as rollers attached to the above-mentioned transmission elements. The transmission element of the second transmission mechanism may include an outer wheel member rotatably mounted around the main shaft. The locking mechanism can make the transfer element of the second transfer mechanism switch between the fixed configuration and the free configuration. In the locked structure (fixed structure), the locking mechanism fixes the transmission element to the main shaft, and in the unlocked structure (free structure), the locking mechanism separates the second motor from the main shaft by releasing the fixed engagement between the transmission element and the main shaft.

In some aspects, the inner ring portion or the flange portion is fixedly arranged or formed around the main shaft, and the transmission element includes a portion rotatably arranged around the inner ring portion. In this mode, the locking mechanism is configured as follows: the outer wheel portion is fixed to the inner wheel portion by the locking mechanism in the above-mentioned locking structure, and the outer wheel portion is separated from the inner wheel portion by the locking mechanism in the unlocking structure. The locking mechanism may include: a rail (second rail) disposed on the outer wheel; a rail (first rail) disposed on the inner wheel; and a locking member operatively connected to the actuator. The actuator is used to fix or separate the outer wheel part relative to the inner wheel part. When the first track and the second track are arranged in a straight line, in the above locking structure, the locking mechanism is fitted with the first track and the second track, In the unlocked structure described above, the lock mechanism releases the fitting of the two rails.

In one embodiment, the second motor is a servo motor that drives a drive shaft that is adjacent to the main shaft and extends in a direction intersecting the axis of the main shaft. The second transmission mechanism has a cam such as a roller gear cam that is attached to the drive shaft and rotates around the axis of the drive shaft. The above-mentioned transmission element of the second transmission mechanism may include an outer wheel member. The outer ring member is rotatably provided around the main shaft by a plurality of rollers mounted around the outer ring member.

In another aspect of the present invention, a machine tool has a spindle, a motor, a transmission mechanism, and a lock mechanism. In order to drive the main shaft with the motor, the transmission mechanism has a transmission element. The transmission element is operatively engaged with the motor, and is rotatably mounted around the main shaft. The locking mechanism is switchable between a locked orientation and an unlocked orientation. In the locking direction, the locking mechanism fixes a rotatably attached transmission element to the main shaft in order to drive the main shaft with the motor via the transmission element. In the unlocking direction, the locking mechanism separates the transmission element from the main shaft by allowing independent rotation of the transmission element relative to the main shaft in order to separate the motor from the main shaft.

In one aspect, the rotatably attached transmission element is a turret unit including a wheel member rotatably attached to the main shaft. The wheel member may include an outer surface portion and a plurality of roller members arranged on the outer surface portion. In one embodiment, each of the roller members includes a rotation shaft, and each of the rotation shafts of the plurality of roller members extends radially outward from the outer surface portion of the wheel member. The various types of transmission mechanisms include a gear cam that drives a roller member when the gear cam is rotated by a motor, and operatively meshes with at least one of the plurality of roller members to rotate the wheel member.

In another aspect of the present invention, a machine tool as a mechanical device includes a main shaft, a first motor, a second motor, a drive shaft, a cam, and a cam follower. The spindle is the part used to turn the workpiece. The first motor rotates the main shaft at relatively high speed. The second motor rotates the main shaft at a relatively low speed. The drive shaft is the drive shaft of the second motor and has an axis. The cam is a cam such as a hobbed cam, and is connected to the drive shaft. Cam followers are mounted radially around the main shaft. To turn the main shaft, the cam engages the cam follower. The machine tool may have a wheel member rotatably mounted around the spindle. Here, a plurality of cam followers in the form of a roller member are attached radially around the wheel member. In one form, a locking mechanism is provided for selectively engaging and disengaging the wheel member with respect to the spindle. The locking mechanism may have a slidable fitting portion movable between an engaged configuration and a non-engaged configuration. In the coupling structure, the slidable fitting portion connects the wheel member to the main shaft. In the non-joint structure, the slidable fitting portion moves in a direction away from the main shaft to separate the wheel member from the main shaft. The locking mechanism may also include a track (second track) connected to the wheel member and a track (first track) connected to the main shaft. When the first rail and the second rail are arranged on a straight line, the slidable fitting part slides along each rail in order to form the joint structure. In one mode, the drive shaft of the second motor is directly connected to the cam, so that the cam rotates around the axis of the drive shaft together with the drive shaft. Although the present invention is not limited to the illustrated embodiments, the present invention will be described based on the illustrated embodiments.

<implementation mode>

As shown in FIGS. 1 and 2 , a lathe (which may be understood as a machine tool) 1 has a frame 2 supporting one or more tool holders 6 (refer to FIG. 3 ) for cutting a workpiece 8 (refer to FIG. 3 ). The main part of the machine tool 1 of this embodiment is referring to the illustrated FIG. 3 , and a metal workpiece 8 such as a pipe is held and rotated by a spindle 10 (which can be understood as a first rotating member). Thus, the cutting tool can cut the rotating workpiece 8 in order to remove, for example, the outer diameter portion of the workpiece 8 (processing by rotation). The machine tool 1 has a spindle drive system 4 . In order to selectively drive a large horizontally oriented spindle 10 with a through-hole diameter of more than 7 inches, the spindle drive system 4 has a large first motor 12 (which can be understood as a first rotating drive part) and a small second motor 14 (can be understood as the second rotation drive part). The spindle 10 holds the large workpiece 8 such that one end of the workpiece 8 protrudes from the spindle 10 . Also, one or more workpiece support tables may be used to support the workpiece 8 along its length. In the illustrated spindle drive system 4, the large first motor 12 is used to drive the spindle 10 during high-speed rotation and high-torque machining, and the small second motor 14 is used for relatively low-speed rotation and relatively high-precision machining. or contour machining.

As shown in FIGS. 1 and 2 , one end of the machine tool 1 has a spindle housing 16 . As shown in FIG. 3 , the spindle housing 16 at least partially houses the spindle 10 and the spindle drive system 4 . The first motor 12 is mounted on the frame 2 , for example as shown in FIGS. 3 , 4 , and 13 . The first motor 12 is operatively connected to the main shaft 10 via a corresponding first transmission mechanism 18 . The first transmission mechanism 18 has a plurality of transmission elements such as a gearbox 20 and gears 22 , 24 , and 26 . The gear box 20 has a plurality of gears, and performs high-speed rotation, medium-speed rotation and separation of the first motor 12 from the main shaft 10 . In one example, the first motor 12 rotates the spindle 10 at 0-1500 RPM in the high-speed rotation mode, and rotates the spindle 10 at 0-500 RPM in the medium-speed rotation mode. However, by using different gear ratios, of course different maximum speeds can be obtained.

The driven gear 26 is attached around the main shaft 10 , and drives the main shaft 10 by meshing with the intermediate gear 24 and the driving gear 22 so as to be operative. The intermediate gear 24 is provided on a shaft 28 and rotates around the shaft 28 . The spindle position feedback sensor 30 and the rotary scale 32 make it possible to perform drive control using the position information of the spindle 10 , so that the movement of the spindle 10 can be accurately controlled. To rotatably support the spindle 10 within the spindle housing 16 , the spindle 10 is mounted in bearings 34 , 36 .

The first transfer mechanism 18 may introduce slight positional inaccuracies within the system due to backlash or backlash in the gears of the transfer mechanism. Therefore, the machine tool 1 of the present embodiment includes the second motor 14 and the second transmission mechanism 38 in addition to the first motor 12 and the first transmission mechanism 18 . The second motor 14 and the second transmission mechanism 38 are used for C-axis contouring (that is, milling the outer surface of the workpiece 8 while rotating the workpiece 8 precisely) or other milling operations that require higher precision. cutting action. That is, the spindle drive system 4 uses a large and high-output first motor (spindle motor) 12 in order to machine the workpiece 8 at a higher speed. Furthermore, for low-speed control of the rotation of the main shaft 10 and further precise control of the position of the main shaft 10, a separate smaller and low-output second motor (servo motor) 14 is used. In one example, the first motor 12 can have at least 1.5 times the rated output of the second motor 14 , and in another example, the rated output of the first motor 12 can be more than 10 times the rated output of the second motor 14 . More specifically, in one example, the first electric machine 12 has a rated output of approximately 60 kW and the second electric machine 14 has a rated output of approximately 4.5 kW. However, motors 12, 14 with different rated outputs may be used. For example, the first electric motor 12 may have a rated output in the range of 10-100 HP, and the second electric motor 14 may reach 4.5-9.5 kW. In addition, the gear ratio used in the first transmission mechanism 18 and the transmission elements of the second transmission mechanism 38 can be changed according to the spindle drive system 4 of the spindle 10 having different sizes or different applications. For example, by selecting different gear ratios, a 60kW motor can be used as the first motor 12 of the main shaft 10 with a through hole diameter of 185mm-375mm, and can have a torque output of 5800N·m-7000N·m.

The spindle drive system 4 of this embodiment is configured to have the same level of accuracy as a spindle drive device without a transmission mechanism, that is, a spindle drive device using a motor integrated with the spindle. However, one of the advantages of the spindle drive system 4 of this embodiment compared with the motor is that the spindle drive system 4 can mount a large spindle 10 having a through-hole diameter exceeding 7 inches. In one example, the spindle 10 of the present embodiment has a through bore diameter of 375 mm or about 15 inches. Therefore, the illustrated spindle drive system 4 maintains high precision equivalent to that of an integrated spindle motor suitable for driving a spindle with a very small through-hole diameter, and can handle very large workpieces 8 .

The second motor 14 is configured to drive the spindle 10 using a second transmission mechanism 38 independent of the first transmission mechanism 18 . In other words, as will be described later, the second motor 14 rotates the turret unit (surrounding portion, which can be understood as a second rotating member) 48 via the gear cam unit 44 . Then, the second motor 14 rotates the main shaft 10 by the rotation of the turret unit 48 . More preferably, the first transmission mechanism 18 and the second transmission mechanism 38 are clearly distinguishable and do not share one transmission element such as a driven gear (for example, the driven gear 26 ) mounted around the main shaft 10 . As an example, the second motor 14 is a servo motor and is provided relative to the main shaft housing 16 . Referring to FIGS. 3 to 5 , the second motor 14 is disposed on one side of the spindle 10 together with the drive shaft 42 . The drive shaft 42 is connected to the second transmission mechanism 38 . The second transmission mechanism 38 (more specifically, the transmission element of the second transmission mechanism 38 ) can optionally be a "fixed structure". When the second transmission mechanism 38 is a fixed structure (that is, when the second transmission mechanism 38 is operatively connected to the main shaft 10 ), the second motor 14 can drive the main shaft 10 . In one example, the selectively fixable transmission element is fixed to the spindle 10 by a lock mechanism 52 described later. The fixed structure refers to a state where the turret unit 48 and the main shaft 10 are connected via the second transmission mechanism 38 . On the other hand, the non-fixed structure refers to a state where the turret unit 48 and the main shaft 10 are not connected by the second transmission mechanism 38 . The locking mechanism 52 can be used to switch the fixed structure and the non-fixed structure of the second transmission mechanism 38 . When the second transmission mechanism 38 is a fixed structure, the second motor 14 makes the main shaft 10 rotate together with the turret unit 48 (that is, the main shaft 10 also rotates by means of the rotation of the turret unit 48 ). On the other hand, when the second transmission mechanism 38 is a non-fixed structure, the second motor 14 rotates the turret unit 48 independently of the main shaft 10 (that is, the turret unit 48 does not rotate the main shaft 10 ).

As shown in FIG. 6 , a turret unit 48 which may be understood as a structural element of the second transmission mechanism 38 includes an outer ring portion 49 having a plurality of cam rollers (or cam followers) 46 . Each cam roller 46 is attached to an outer surface portion 49 a as a circumference of the outer ring portion 49 along the radial direction (rotation radius direction of the turret unit 48 ). The rotational axis of each cam roller 46 extends in this radial direction of the turret unit 48 . The second transmission mechanism 38 has a cam such as a hobbed cam unit 44 (see FIG. 5 ). The hobbing cam unit 44 is installed coaxially with the drive shaft 42 and arranged on a straight line with the drive shaft 42 . As will be described in detail below, the gear cam unit 44 is configured to mesh with a plurality of cam rollers 46 at the same time. The turret unit 48 (shown in FIG. 3 ) is rotatably mounted around the main shaft 10 via a bearing housing 50 and coaxially mounted with the main shaft 10 . That is, as shown in FIGS. 3 and 4 , the turret unit 48 surrounds a part of the main shaft 10 , the main shaft 10 rotates about the rotation axis AX, and the turret unit 48 also rotates about the same rotation axis AX. Thus, while the turret unit 48 is not connected or fixed to the main shaft 10 by means of the locking mechanism 52 (non-fixed configuration), the main shaft 10 is able to rotate relative to the turret unit 48 (and vice versa).

The hobbing cam unit 44 shown in FIG. 5 , FIG. 9 , FIG. 14 , etc. has a central driving portion. The central drive has a threaded or helical cam surface formed by continuous wedge ribs. The rib protrudes from the shank and extends around the shank in a helical path. The threaded or helical cam surface provides smooth and backlash-free driving contact with the cam roller 46 . In a preferred example, in order to increase the efficiency of the second transmission mechanism 38, the shank of the hobbing cam unit 44 has the same concave profile (appearance) as the drum worm. As shown in FIG. 5, the hob cam unit 44 has shaft portions 44a, 44b extending axially from the central driving portion. And, each shaft part 44a, 44b is supported by bearing 40a, 41a in the vicinity of each end part of shaft part 44a, 44b. As shown in FIG. 4 , the bearings 40 a, 41 a are contained in bearing housings 40 , 41 , and the central drive portion of the hobbing cam unit 44 is located in a housing 45 . In addition, the hob cam unit 44 is provided with an opening in the housing 45 so as to be able to engage with the cam roller 46 . Torque is transmitted from the hob cam unit 44 by the rotational motion of the cam roller 46 . Cam rollers 46 are formed between adjacent portions of the cam surfaces of the helical ribs, driven along a helical path whereby the hobbing cam unit 44 (when viewed from above the second motor 14 ) moves clockwise direction, whereby the turret unit 48 rotates in a clockwise direction as shown in FIG. 10 . In the illustrated manner, 60 cam rollers 46 are equally arranged around the circumference of the outer ring portion 49 of the turret unit 48 . Each cam roller 46 is rotatable around an axis arranged along the radial direction extending from the center of the turret unit 48 through the center of each cam roller 46 (see FIG. 6 ). The necessary number of cam rollers 46 is determined based on the size of the main shaft 10 and other performance considerations known in the art.

The turret unit 48 is operatively engaged with the main shaft 10 , and is provided with a locking mechanism 52 so that the second motor 14 can drive the main shaft 10 . Here, the locking mechanism 52 will be further described in detail. The locking mechanism 52 as an example has a plurality of coupling elements (constituent elements including the first rail 58 and the second rail 56 ) that are operatively connected to the main shaft 10 and the turret unit 48 . In order to fix the turret unit 48 to the main shaft 10, when the connecting elements (referring to Fig. 6, Fig. 7, Fig. 11, more specifically the first rail 58 and the second rail 56) are arranged on a straight line with each other, it can be selectively The main shaft 10 and the turret unit 48 are ground connected. When the coupling elements are arranged on a straight line, the axes of the aligned coupling elements extend along the radial direction relative to the circumference of the main shaft 10 (which can be understood as the radius of rotation of the main shaft 10 ). Thereafter, for example, referring to FIG. 7 , the fitting member 66 straddles the first rail 58 and the second rail 56 and moves toward the center of the main shaft 10 along the axes of the first rail 58 and the second rail 56 extending in the above-mentioned radial direction ( slide). Thus, the first rail 58 and the second rail 56 are fixed in a state of being aligned on a straight line (that is, it can be understood as the first state in which the fitting member 66 is fitted to the first rail 58 and the second rail 56). Here, both the main shaft 10 and the turret unit 48 are fixed (the above-mentioned fixed structure). As a result, the second electric motor 14 can drive the spindle 10 by means of the turret unit 48 and the locking mechanism 52 .

The locking mechanism 52 illustrated in FIG. 6 has a first track 58 , a second track 56 and a third track 54 . The first track 58 is disposed on the main shaft 10 . The main shaft 10 has an annular flange (hereinafter referred to as inner ring member 64 ) fixedly attached to the outer peripheral surface of the main shaft 10 . The first rail 58 is attached to the inner wheel member 64 . The second track 56 is provided on the turret unit 48 surrounding the main shaft 10 . The turret unit 48 has an annular flange (hereinafter referred to as the outer ring member 62 ) fixedly provided on the end surface of the turret unit 48 . The second rail 56 is attached to the outer wheel member 62 . The inner wheel member 64 has an outer diameter that is slightly smaller than the inner diameter of the outer wheel member 62 . Therefore, the outer ring member 62 is arranged coaxially around the inner ring member 64 . For example, as shown in FIG. 6 and the like, when the main shaft 10 is at a predetermined rotational position, the first rail 58 , the second rail 56 , and the third rail 54 are arranged on the same straight line. Furthermore, as shown in FIG. 3 , a bearing housing 50 is installed between the main shaft 10 (more specifically, the inner wheel member 64 ) and the turret unit 48 . Therefore, as will be described later, when the first rail 58 and the second rail 56 are connected without sliding the fitting member 66 (more specifically, the fitting member 66 is not fitted with the first rail 58 but is fitted with the second rail 58). When the two rails 56 are fitted, it can be understood as the second state), the main shaft 10 and the turret unit 48 are not connected (more specifically, the inner wheel member 64 and the outer wheel member 62 are not connected), the main shaft 10 and the turret unit 48 utilize The bearing housings 50 are free to rotate relative to each other. The third rail 54 is attached to the spindle housing 16 (see FIG. 3 ). That is, the first rail 58 rotates together with the rotation of the spindle 10 , and the second rail 56 rotates together with the rotation of the turret unit 48 , but the third rail 54 is fixedly attached to the machine tool 1 and remains stationary. In addition, in the second state, the fitting member 66 is not fitted to the first rail 58 but is fitted to the second rail 56 and the third rail 54 .

The locking mechanism 52 also has a fitting member 66 . As shown in FIG. 6 , the fitting member 66 has a substantially C-shaped cross-section, is fitted to each of the rails 54 , 56 , and 58 , and slides on each of the rails 54 , 56 , and 58 . The fitting member 66 is a linear motion guide that slides along the first rail 58 , the second rail 56 and the third rail 54 . As described above, in the unlocking direction of the lock mechanism 52 (in the second state), the fitting member 66 exists on the third rail 54 and the second rail 56 . Thereby, as shown in FIGS. 6 , 11 , and 12 , the connection between the first rail 58 and the second rail 56 by the fitting member 66 is released, and the second transmission mechanism 38 is independently and operatively separated from the main shaft 10 . Therefore, in the second state, the first motor 12 rotates the main shaft 10 . The first motor 12 is rotated until the main shaft 10 reaches the prescribed position, that is, the 12 o'clock direction of the first track 58 above the main shaft 10 (which can be understood as a prescribed rotational position) is arranged on a straight line with the second track 56, so that the second The motor 14 is capable of driving the spindle 10 (for example, the first motor 12 rotates the spindle 10 so as to change from the state of FIG. 14 to the state of FIG. 13 ). Thereafter, the fitting member 66 slides downward using an actuator such as a hydraulic actuator (which can be understood as a driving portion) 68, so that the fitting member 66 is disposed on the first rail 58 and the second rail 56 (ie, so that The fitting member 66 is fitted to the first rail 58 and the second rail 56 (first state), see FIGS. 7 and 8 ). Thus, as shown in FIGS. 7 and 8 , the fitting member 66 no longer exists on any part of the third rail 54 . After the fitting member 66 moves to a predetermined position where the first rail 58 and the second rail 56 are aligned, the gearbox 20 separates the first motor 12 independently and operatively from the main shaft 10 before being driven by the second motor 14 . (The first transmission mechanism 18 is in the neutral position). For balance relative to the locking mechanism 52 , one or more additional first tracks 60 may be spaced from the first track 58 to the inner wheel member 64 . For example, as shown in FIGS. 4 and 15 , the additional first rail 60 is disposed on the opposite side of the first rail 58 on the annular inner ring member 64 .

For example, as shown in FIGS. 8-10, 12-14, etc., the hydraulic actuator 68 is fixed to the spindle housing 16 (machine tool 1). In addition, as shown in FIG. 6 , for example, the hydraulic actuator 68 has a contact portion 70 and the fitting member 66 has a convex portion 72 . The abutting portion 70 selectively engages with the convex portion 72 . As shown in FIG. 6 , the abutting portion 70 has a concave shape that engages with the convex portion 72 . To shift the locking mechanism 52 to the locked state, the hydraulic actuator 68 drives down the shifting abutment 70 , which presses the fitting member 66 toward the first rail 58 by pressing the protrusion 72 downward. As shown in FIG. 6 , the abutting portion 70 may have a cam follower 74 at a portion abutting against the convex portion 72 . The cam follower 74 is mounted so as to be rotatable around an axis parallel to the axis of the main shaft 10 in the concave shape of the abutting portion 70 in order to abut against the upper surface of the convex portion 72 . If the fitting member 66 is completely present on the first rail 58 and the second rail 56 , the outer wheel member 62 is fixed to the inner wheel member 64 , whereby the turret unit 48 of the second transmission mechanism 38 is fixed to the main shaft 10 . Thus, the turret unit 48 can rotate together with the main shaft 10 . Therefore, as shown in FIG. 10 , in the first state (fixed structure), the second motor 14 is operatively engaged with the main shaft 10 , and the second motor rotates the turret unit 48 , thereby using the rails 56 , 58 to rotate. and the fitting member 66 to drive the main shaft 10 .

The fitting member 66 exists on the second rail 56 and the first rail 58, and by the rotation of the main shaft 10 driven by the second motor 14, the hydraulic pressure is applied during the rotation of the fitting member 66 together with the inner wheel member 64 and the outer wheel member 62. The actuator 68 remains in the extended position (see FIG. 10 ). In this state, when the fitting member 66 returns to the above-mentioned predetermined position, the abutting portion 70 can make the fitting member 66 retreat upward and return to the initial position on the third rail 54 and the second rail 56, using hydraulic pressure. The actuator 68 positions the abutment 70 . The abutting portion 70 is capable of abutting against the convex portion 72 in the rotational radius direction of the main shaft 10 and the like, and does not abut against the convex portion 72 in the rotational direction of the main shaft 10 and the like. That is, since the contact portion 70 has a concave shape, the convex portion 72 can pass between the legs of the concave portion of the contact portion 70 even when the spindle 10 is rotated by the second motor 14 as in milling, for example. Although the cam follower 74 included in the abutting portion 70 contacts the convex portion 72 when the convex portion 72 passes the abutting portion 70, the cam follower 74 will reduce the distance between the two members 72, 74 at the time of contact. Contact resistance is suppressed to a minimum.

In order to separate the second motor 14 and the second transmission mechanism 38 from the main shaft 10, the main shaft 10 needs to be rotated by the second motor 14 until the second rail 56, the first rail 58 and the fitting member 66 return to a prescribed position. At predetermined positions, the rails 54 , 56 , 58 are aligned on a straight line, and the hydraulic actuator 68 can perform a lifting operation. That is, as shown in FIGS. 11 and 12 , the fitting member 66 is lifted by the abutment portion 70 (second state, non-fixed structure), until the fitting member 66 returns to the initial position on the third rail 54 and the second rail 56 (corresponding to the unlocking direction of the locking mechanism 52). In order to confirm the return of the fitting member 66 to the aforementioned position, a position sensor may also be used. Thereafter, the first motor 12 shifts from the neutral state of the gear box 20 to the high-speed operation mode or the medium-speed operation mode. Afterwards, as shown in FIGS. 13 and 14 , the first motor 12 drives the main shaft 10 through the first transmission mechanism 18 .

The machine tool 1 of the present embodiment includes: a main shaft 10 that rotates about a rotation axis AX; and a turret unit 48 that surrounds the main shaft 10 . Furthermore, this machine tool 1 includes a first rail 58 , a second rail 56 and a fitting member 66 . The fitting member 66 moves along the first rail 58 and the second rail 56 . Also, the fitting member 66 is fitted to the first rail 58 and the second rail 56 in the first state. In addition, the fitting member 66 is not fitted to the first rail 58 but fitted to the second rail 56 in the second state.

Accordingly, the fitting member 66 can move along the first rail 58 and the second rail 56 from the second state to the first state. That is, a structure in which the fitting member 66 is fitted to the first rail 58 and the second rail 56 and the main shaft 10 is fixed to the turret unit 48 can be realized. In this way, since the fitting member 66 is fitted to the first rail 58 and the second rail 56, it is possible to prevent a gap from being generated between the fitting member 66 and the respective rails 58, 56 (in other words, it is possible to prevent backlash or the like from being generated). . Therefore, since the rotation of the spindle 10 can be controlled with high precision, the workpiece 8 can be machined accurately and with high precision.

In addition, in the machine tool 1 of the present embodiment, the fitting member 66 slides on the first rail 58 and the second rail 56 .

Therefore, it is possible to smoothly move the fitting member 66 on each of the rails 56 , 58 without causing play or the like between the fitting member 66 and each of the rails 56 , 58 . Therefore, mechanical abrasion of the fitting member 66 and each rail 56, 58 can be suppressed.

In addition, in the machine tool 1 of the present embodiment, the turret unit 48 rotates about the rotation axis AX, and can rotate independently of the main shaft 10 .

Therefore, in the first state, the main shaft 10 and the turret unit 48 can be rotated together, and in the second state, the main shaft 10 and the turret unit 48 can be rotated independently.

In addition, in the machine tool 1 of the present embodiment, the first rail 58 is provided on the main shaft 10 along the radius of rotation of the main shaft 10 . Also, the second rail 56 is provided on the turret unit 48 along the turning radius.

Therefore, a structure may be adopted in which the fitting member 66 is moved in the direction of the radius of rotation, and the transition between the first state and the second state can be realized by the movement in the direction of the radius of rotation.

Furthermore, the machine tool 1 of the present embodiment includes a third rail 54 fixedly attached to the machine tool 1 .

In this way, since the installation position of the third rail 54 is fixed, the third rail 54 can be used as a mark of a predetermined rotational position where the first rail 58 and the second rail 56 are arranged on the same straight line. That is, in the machine tool 1 , for example, when it is necessary to set the rotation position, the setting and the like can be easily performed by using the third rail 54 .

In addition, the machine tool 1 of the present embodiment further includes a hydraulic actuator 68 for moving the fitting member 66 . Furthermore, the fitting member 66 has a convex portion 72 . The hydraulic actuator 68 has an abutment 70 . The abutting portion 70 is capable of abutting against the convex portion 72 in the rotational radius direction. The contact portion 70 does not contact the convex portion 72 in the rotation direction of the spindle 10 . For example, the abutting portion 70 has a concave portion shape 70A that engages with the convex portion 72 .

Therefore, by bringing the hydraulic actuator 68 into contact with the convex portion 72 in the rotational radius direction, the hydraulic actuator 68 can move the fitting member 66 on each of the rails 56 , 58 by contacting the convex portion 72 . In addition, in the first state, the hydraulic actuator 68 does not hinder the rotation of the respective rails 56 , 58 and the fitting member 66 accompanying the rotation of the main shaft 10 . Therefore, the hydraulic actuator 68 does not need to be installed in the rotating system including the main shaft 10, but can be installed in the fixed system. That is, the hydraulic actuator 68 can be prevented from rotating together with the main shaft 10 . Therefore, simplification of the structure including the hydraulic actuator 68 can be achieved, thereby preventing adverse phenomena due to the rotation of the hydraulic actuator 68 .

In addition, in the machine tool 1 according to Embodiment 1, the hydraulic actuator 68 has the cam follower 74 provided on the portion of the hydraulic actuator 68 that contacts the convex portion 72 .

Therefore, impact and wear at the contact portion of the hydraulic actuator 68 and the convex portion 72 accompanying the rotation of the main shaft 10 can be prevented.

In addition, the machine tool 1 of the present embodiment further includes a hobbing cam unit 44 , and a turret unit 48 has a plurality of cam followers 46 meshing with the hobbing cam unit 44 .

Therefore, the turret unit 48 can be rotated without play or the like. Therefore, the turret unit 48 can be rotated accurately and with high precision.

In addition, the machine tool 1 of this embodiment further includes a first motor 12 and a second motor 14 . The first motor 12 rotates the main shaft 10 . The second electric motor 14 turns the spindle 10 by means of the turret unit 48 . For example, the first motor 12 rotates the spindle 10 faster than the second motor 14 rotates the spindle 10 .

Therefore, by rotating the main shaft 10 with the second motor 14 in the first state, high-precision machining using slow rotation can be performed. In addition, in the second state, by rotating the main shaft 10 with the first motor 12, machining using high-speed rotation can be performed.

The present invention has been described in association with preferred embodiments, but those skilled in the art can understand the details of the components and structural elements described and illustrated for explaining the nature of the present invention within the principle and scope of the present invention. , materials and arrangements are subject to various changes.

Claims (15)

1. a kind of lathe, is the lathe (1) for carrying out the processing using rotation, it is characterised in that including：

First tumbler (10), is rotated centered on rotary shaft (AX)；

Around portion (48), around first tumbler；

First track (58), is arranged at first tumbler；

Second track (56), by defined turned position and first track configurations on the same line in the way of, set Portion is surrounded in described；And

Fitting member (66), is moved along first track and second track, and in the first state with described One track and second track are chimeric, not chimeric with first track in the second condition but embedding with second track Close.

2. lathe according to claim 1, it is characterised in that the fitting member is in first track and described second Slided on track.

3. lathe according to claim 1, it is characterised in that the portion that surrounds is the second tumbler (48), described second Tumbler (48) is rotated centered on the rotary shaft, and is arranged to be turned independently of first tumbler It is dynamic.

4. lathe according to claim 3, it is characterised in that

The radius of gyration of first track along first tumbler is arranged at first tumbler,

Second track is arranged at second tumbler along the radius of gyration.

5. lathe according to claim 3, it is characterised in that the lathe includes the 3rd track (54), the 3rd rail Road (54) in the defined turned position and second track configurations, into same linear mode, to be installed on the machine Bed.

6. lathe according to claim 4, it is characterised in that

The lathe also includes making the drive division (68) of the fitting member movement,

The fitting member has convex portion (72),

The drive division has abutting part (70), and the abutting part (70) can be with the convex portion on the radius of gyration direction Abut, and do not abutted in the rotation direction of first tumbler with the convex portion.

7. lathe according to claim 6, it is characterised in that the drive division is fixedly arranged at the lathe.

8. lathe according to claim 7, it is characterised in that the abutting part has the recess shape engaged with the convex portion Shape (70A).

9. lathe according to claim 6, it is characterised in that the drive division has cam follower (74), described convex Wheel driven member (74) is arranged on the part abutted with the convex portion of the drive division.

10. the lathe according to any one in claim 3 to 9, it is characterised in that

The lathe also includes gear hobbing cam (44),

Second tumbler has multiple cam followers (46) with the gear hobbing cam-engaged.

11. the lathe according to any one in claim 3 to 9, it is characterised in that also include：

First rotates drive division (12), rotates first tumbler；And

Second rotates drive division (14), and first tumbler is rotated by second tumbler.

12. lathe according to claim 11, it is characterised in that the first rotation drive division makes first tumbler The speed of rotation is faster than the speed that the described second rotation drive division rotates first tumbler.

13. lathe according to claim 12, it is characterised in that described second rotates drive division in said first condition By rotating second tumbler, so as to make institute by first track, second track and the fitting member The first tumbler is stated also to rotate.

14. lathe according to claim 12, it is characterised in that described first rotates drive division in said second condition Rotate first tumbler.

15. lathe as claimed in any of claims 1 to 9, it is characterised in that first tumbler keeps workpiece (8)。